JP2005037037A - Heat exchanger - Google Patents

Abstract

<P>PROBLEM TO BE SOLVED: To reduce the capacity of a header tank by reducing an inner diameter in the air flowing direction of the header tank, and to improve the heat exchanging performance. <P>SOLUTION: The inner diameter in the air flowing direction of the header tank 5 is determined to be less than a width of a tube 2, a ratio of the inner diameter in the air flowing direction of the header tank 5 to the width of the tube 2 is determined to be 0.7 or more. The header tank 5 is composed of the combination of a first member 15 and a second member 16. A tube insertion hole 15c is formed from a tube insertion-side wall part 15a to a flange 15b of the first member 15. The tube 2 is inserted into the tube insertion hole 15c to communicate the tube 2 and the header tank 5. <P>COPYRIGHT: (C)2005,JPO&NCIPI

Description

  The present invention relates to a heat exchanger used in, for example, an air conditioner.

  2. Description of the Related Art Conventionally, a heat exchanger has a plurality of flat tubes arranged in a direction intersecting with an air flow direction, and tubular header tanks are disposed at both ends of the tubes, respectively. By inserting the end of the tube into the insertion hole, the tube and the header tank are communicated, and when the refrigerant flows into one of the header tanks, the refrigerant is divided into each tube and flows through the tube. After gathering in the header tank, it flows out to the outside.

  By the way, in recent years, there is a demand for reducing the charging amount of the refrigerant in the equipment in consideration of the environment in the equipment using the refrigeration cycle such as an air conditioner. In order to satisfy this requirement, it is conceivable to reduce the internal volume of the header tank. However, simply by reducing the internal volume by simply reducing the diameter of the header tank, the tube is inserted into the header tank. The outer dimension in the air flow direction must be shortened, the heat transfer area of the tube is reduced, and the heat exchange efficiency is deteriorated.

Therefore, in order to avoid this, the header tank has a flat cross section that is long in the air flow direction, so that the outer dimensions of the tube in the air flow direction can be ensured without deteriorating the heat exchange efficiency. A heat exchanger (condenser) has been developed in which the internal volume of the refrigerant is made smaller than that of a true circular cross section so that the refrigerant charging amount can be reduced (see, for example, Patent Document 1).
JP-A-9-113177 (4th page, 5th page, FIG. 1, FIG. 3)

  By the way, in the heat exchanger of patent document 1, although the internal volume is small by the part which made the cross section of the header tank long and flat in the air flow direction, the inner diameter of the air flow direction of the header tank is the air flow direction of the tube. It is set longer than the outer dimensions of the header tank, and the capacity of the header tank is not sufficiently reduced.

  The present invention has been made in view of such points, and the object of the present invention is to transfer the tube even if the inner diameter dimension of the header tank in the air flow direction is shorter than the outer dimension of the tube in the air flow direction. The heat exchange efficiency is improved by ensuring the heat area and the amount of refrigerant flowing into the tube.

  In order to achieve the above object, in the inventions of claims 1 and 2, a plurality of flat tubes whose cross-sectional shapes are long in the air flow direction are juxtaposed in a direction crossing the air flow direction, and the ends of these tubes are connected to the tube. It is intended for a heat exchanger that is inserted into a cylindrical header tank that extends in the juxtaposed direction to communicate each tube with the inside of the header tank.

  In the first aspect of the invention, the inner diameter dimension of the header tank is made shorter than the outer dimension of the tube in the air flow direction, the protrusion is formed on the outer peripheral wall portion of the header tank, and the tube insertion hole continuous to the protrusion. The ratio of the inner diameter dimension of the header tank to the outer dimension of the tube was set so that the refrigerant inflow amount from the inside of the header tank to the tube could be secured.

  Specifically, the header tank is formed such that a ratio of an inner diameter dimension in the air flow direction of the header tank to an outer dimension in the air flow direction of the tube is less than 1 and 0.7 or more, The outer peripheral wall is provided with a protruding portion that protrudes outward on the upstream and downstream sides in the air flow direction, and a tube insertion hole that continues to the protruding portion, and the end of the tube is inserted into the tube insertion hole And

  According to this configuration, the inner diameter dimension of the header tank in the air flow direction is shorter than the outer dimension of the tube in the air flow direction, thereby reducing the capacity of the header tank. When the capacity of the header tank is reduced in this way, the outer dimension of the tube in the air flow direction is set to be longer than the inner diameter dimension of the header tank in the air flow direction. It is done.

  In the state where the end of the tube is inserted into the tube insertion hole, the portion other than the portion inserted into the portion of the opening at the end of the tube that is continuous with the protruding portion of the tube insertion hole faces the inside of the header tank, The header tank communicates. At this time, since the ratio of the inner diameter dimension of the header tank to the outer dimension of the tube in the air flow direction is 0.7 or more, 70% or more of the entire opening of the tube faces the inside of the header tank. Refrigerant flows from the area. By setting the area of the tube opening facing the inside of the header tank in this way, the amount of refrigerant flowing into the tube is hardly reduced compared to the case where the entire opening faces the header tank. The amount of refrigerant inflow for the season is secured.

  According to the second aspect of the present invention, the inner diameter dimension of the header tank is made shorter than the outer dimension of the tube in the air flow direction, a hollow projecting portion is formed on the outer peripheral wall portion of the header tank, and the tube continuous to the projecting portion. An insertion hole was provided so that the opening at the end of the tube communicated with the inside of the header tank through the inside of the protruding portion.

  Specifically, the header tank is formed such that the inner diameter dimension in the air flow direction is shorter than the outer dimension in the air flow direction of the tube, and the outer peripheral wall portion of the header tank has an upstream side in the air flow direction. And a hollow projecting portion projecting outward on the downstream side and communicating with the inside of the header tank, and a tube insertion hole continuing to the projecting portion, the end portion of the tube being disposed at an opening of the end portion. It is set as the structure inserted in the said tube insertion hole so that it may communicate with the inside.

  According to this configuration, since the inner diameter dimension of the header tank in the air flow direction is shorter than the outer dimension of the tube in the air flow direction, the capacity of the header tank can be reduced. When the capacity of the header tank is reduced in this way, the outer dimension of the tube in the air flow direction is longer than the inner diameter dimension of the header tank in the air flow direction. A sufficient heat transfer area can be obtained.

  And in the state which inserted the edge part of the tube in the tube insertion hole, the location inserted in the part which continues to the protrusion part in a tube insertion hole among the opening of the tube end part via the inside of a protrusion part is a header tank. It communicates with the inside, and other parts face the header tank. Thereby, since the refrigerant | coolant of a header tank flows in into this tube from the whole opening of a tube, the refrigerant | coolant inflow amount to a tube is ensured.

  In the invention of claim 3, in the invention of claim 2, a step portion extending outward from the tube insertion hole is provided at the proximal end of the tube insertion hole to the tube insertion hole, and is inserted into the tube insertion hole. The tube is positioned so that the stepped portion engages with the periphery of the tube insertion hole and the opening at the end of the tube communicates with the inside of the protruding portion.

  According to this configuration, when the tube is inserted into the tube insertion hole, the stepped portion of the tube is engaged with the periphery of the tube insertion hole, and further insertion of the tube is restricted. At this time, the end portion of the tube Is in a state of communicating with the hollow portion of the protrusion. Thereby, the opening of the tube can be reliably communicated with the hollow portion of the protruding portion without positioning the tube using a jig or the like.

  In the invention of claim 4, in any one of claims 1 to 3, the end of the tube is brazed to the periphery of the tube insertion hole, and the tube insertion side wall of the header tank is opposed to the tube insertion side wall. The anti-tube insertion side wall portion is formed in a curved surface shape that bulges outward from the header tank, and the tube insertion side wall portion is flatter than the anti-tube insertion side wall portion.

  According to this configuration, since substantially the entire outer peripheral wall portion of the header tank is configured by a curved surface, the pressure resistance of the header tank is ensured while thinning the constituent members of the header tank. Moreover, since the tube and the tube insertion side wall are integrated by brazing the end of the tube to the periphery of the tube insertion hole, the strength of the tube insertion side wall is higher than that of the anti-tube insertion side wall. This tube insertion side wall portion is formed relatively flat, so that the capacity of the header tank can be further reduced.

  In the invention of claim 5, in the invention of claim 4, the header tank is constituted by a combination of a first member having a tube insertion side wall portion and a second member having an anti-tube insertion side wall portion.

  According to this structure, a header tank is comprised by combining after forming a 1st member and a 2nd member separately, for example by press work.

  According to the invention of claim 6, in the invention of claim 5, a brazing material is provided on the contact surface of the first member with the second member, while no brazing material is provided on the second member.

  According to this configuration, by heating in a state where the first member and the second member are combined, the brazing material of the first member is melted and the first member and the second member are brazed. At this time, for example, when the end of the tube comes into contact with the second member due to a manufacturing error or the like, the brazing material flows into the opening at the end of the tube because the brazing material is not provided on the second member. There is no.

  In the invention of claim 7, in the invention of claim 5 or 6, the protruding portion protruding from the outer peripheral wall portion of the header tank is constituted by a flange extending facing the first member and the second member, and the tube insertion hole is formed. The tube is formed continuously from the tube insertion side wall portion of the first member to the flange, the peripheral portion of the tube insertion hole in the flange of the first member, and the portion facing the peripheral edge of the tube insertion hole in the flange of the second member At least one of them is formed in a concave shape so as to have a space between them, and the end of the tube inserted into the tube insertion hole is projected from the tube insertion hole and positioned in the space.

  According to this configuration, the flanges of the first member and the second member are joined, and the first member and the second member are integrated. Further, a space is formed between the peripheral portion of the tube insertion hole of the flange of the first member and the flange of the second member, and the opening of the end portion of the tube is positioned in this space. For this reason, when the brazing material provided in the first member or the second member melts during brazing and flows through the flange, the brazing material does not flow to the opening at the end of the tube.

  In the invention of claim 8, in the invention of claim 7, at least one flange of the first member and the second member is provided with a caulking portion that is caulked and fixed to the other flange.

  According to this configuration, one flange of the first member and the second member is caulked and fixed to the other, and the first member and the second member are combined to prevent mutual displacement.

  In the invention of claim push 9, in invention of claim 8, it is set as the structure which provides a crimping part corresponding to the part which the flange of the 1st member and the 2nd member joins mutually.

  According to this structure, it brazes in the state which the junction part of the flange of the 1st member and the 2nd member contacted reliably.

  According to the first aspect of the present invention, the ratio of the inner diameter dimension of the header tank to the outer dimension of the tube in the air flow direction is less than 1, and the projecting portion projecting outward is provided on the outer peripheral wall portion of the header tank. Since the end of the tube is inserted into the tube insertion hole formed continuously, the inner diameter of the header tank is smaller than the outer dimension of the tube in the air flow direction, further increasing the inner volume of the header tank. While being able to reduce, the external dimension of a tube is ensured and the heat-transfer area of a tube can fully be obtained. In addition, since the ratio of the inner diameter dimension of the header tank to the outer dimension of the tube in the air flow direction is 0.7 or more, the refrigerant flows from 70% or more of the entire opening at the end of the tube. Thereby, the refrigerant | coolant inflow amount to a tube is ensured and heat exchange efficiency can be improved.

  According to the second aspect of the present invention, the inner diameter dimension of the header tank in the air flow direction is made smaller than the outer dimension of the tube in the air flow direction, and protrudes outward from the outer peripheral wall portion of the header tank so as to communicate with the inside of the header tank. In the same manner as in the first aspect of the present invention, the inner volume of the header tank is provided with a cylindrical projection and a tube insertion hole continuous with the projection, and the opening at the end of the tube communicates with the interior of the projection. Can be further reduced, and the heat transfer area of the tube can be sufficiently obtained. And since the refrigerant | coolant of a header tank flows in into this tube from the whole area | region of opening of a tube, the refrigerant | coolant inflow amount to a tube is ensured, Therefore Heat exchange efficiency can be improved.

  According to the third aspect of the present invention, the step is formed at the end of the tube, and the step is engaged with the peripheral edge of the tube insertion hole so that the tube is positioned. The opening can be brought into a state of reliably communicating with the hollow portion of the protruding portion, whereby the tube assembling work can be easily performed.

  According to invention of Claim 4, since the tube insertion side wall part and anti-tube insertion side wall part of the header tank were formed in the curved surface shape, a lightweight and high pressure | voltage resistant header tank can be obtained. In addition, since the tube insertion side wall portion where the end portion of the tube is brazed and the strength is ensured has a relatively flat shape, the inner volume of the header tank can be further reduced without increasing the thickness of the tube insertion side wall portion. can do.

  According to the fifth aspect of the present invention, the tube insertion side wall portion and the anti-tube insertion side wall portion having different shapes can be separately formed, thereby making it easier than the case where the header tank is integrally formed into a cylindrical shape. Can be molded.

  According to the sixth aspect of the present invention, the brazing material is provided on the contact surface of the first member with the second member, while the brazing material is not provided on the second member. When the portion comes into contact with the second member, the brazing material does not flow to the opening at the end of the tube, and the opening can be prevented from being blocked by the brazing material, and the refrigerant can flow as intended. .

  According to invention of Claim 7, the protrusion part of a header tank is comprised by the flange of a 1st member and a 2nd member, a tube insertion hole is continuously formed from the tube insertion side wall part of a 1st member to a flange, A space is formed between the peripheral edge portion of the tube insertion hole in the flange of the one member and the flange of the second member, and the end of the tube is positioned in the space. When flowing through the flange, the opening of the end of the tube can be prevented from being blocked by the brazing material, and the refrigerant can flow in as intended.

  According to the eighth aspect of the present invention, since at least one flange of the first member and the second member can be caulked and fixed to the other flange, the first member is caused, for example, by vibration when being carried into the furnace in the brazing process. And the 2nd member does not shift and brazing can be ensured.

  According to invention of Claim 9, the junction part of the flange of a 1st member and a 2nd member can be brazed reliably.

  Hereinafter, embodiments of the present invention will be described in detail with reference to the drawings.

Embodiment 1 of the Invention
FIG. 2 shows a heat exchanger according to an embodiment of the present invention. In this embodiment, the heat exchanger is a condenser 1 constituting one element of a refrigeration cycle of a vehicle air conditioner. Although not shown, the condenser 1 is disposed at the front end portion of the engine room of the vehicle body, and includes a core 4 formed by alternately arranging a plurality of tubes 2 and fins 3 extending in the vehicle width direction. The core 4 includes a header tank 5 on the left side in the vehicle width direction and a header tank 6 on the right side, which are arranged at both ends in the longitudinal direction of the tube 2 and communicate with the tube 2. In the core 4 of the condenser 1, air flows from the front of the vehicle body to the rear as shown by arrows A in FIGS. 1 and 5.

  Each tube 2 of the core 4 is a flat tube having a rectangular cross section that is long in the longitudinal direction of the vehicle body. On the other hand, the fin 3 is a corrugated fin formed so as to have a waveform when viewed from the air flow direction, and extends over both longitudinal ends of the tube 2. These tubes 2 and fins 3 are formed by molding a thin plate material made of an aluminum alloy, and the plate material constituting the tube 2 is a so-called clad material in which brazing materials are provided in layers on the surface thereof.

  As shown in FIG. 3, the separation distance between the adjacent tubes 2 corresponds to the vertical dimension of the fin 3, and the upper end of the fin 3 is brazed to the lower surface of the adjacent tube 2 on the upper side, The lower end of the fin 3 is brazed to the upper surface of the tube 2 adjacent to the lower side. Further, the fins 3 and 3 positioned at the upper end and the lower end of the core 4 are held by upper and lower end plates 8 and 9, respectively.

  The left and right header tanks 5 and 6 are formed in a cylindrical shape extending straight across both ends of the core 4 in the juxtaposition direction of the tube 2 and the fin 3, and the openings at the upper and lower ends are respectively closed by the cap members 10 and 10. Has been. A refrigerant inflow pipe 11 through which refrigerant flows into the condenser 1 is connected to the upper part of the left header tank 5, while a refrigerant outflow pipe 12 through which refrigerant flows out to the outside is connected to the lower part of the right header tank 6. It is connected.

  The inner diameter dimension in the air flow direction of the left and right header tanks 5 and 6 is formed to be shorter than the width dimension of the tube 2, that is, the outer dimension in the air flow direction. Specifically, the ratio of the inner diameter dimension in the air flow direction of the header tanks 5 and 6 to the width dimension of the tube 2 is less than 1, and in this embodiment, the ratio is in the range of 0.7 or more. Is set.

  The left and right header tanks 5 and 6 are each divided into two at the center in the vehicle width direction. The left header tank 5 is configured by a combination of a first member 15 located on the core 4 side and a second member 16 on the opposite side, and the right header tank 6 is similarly formed of the first member 18 and the second member 19. It is composed of a combination. The first members 15 and 18 and the second members 16 and 19 are formed by pressing a plate made of an aluminum alloy by pressing. The first members 15 and 18 are made of a clad material in which a brazing material is provided on the surfaces of the second members 16 and 19, while the second members 16 and 19 are not provided with a brazing material. The first member 15 of the left header tank 5 and the first member 18 of the right header tank 6 are configured similarly, and the second member 16 of the left header tank 5 and the second member of the right header tank 6 are configured. Since 19 is configured in the same manner, the structure of the first member 15 and the second member 16 of the left header tank 5 will be described below.

  The first member 15 has a tube insertion side wall 15a for inserting and holding the tube 2, and the tube insertion side wall 15a is curved so as to bulge outward from the header tank 5 as shown in FIG. It is formed in a bowl shape that opens to the second member 16 side. The cross-sectional shape of the tube insertion side wall 15a is a relatively flat and generally arcuate shape. A pair of flanges 15b and 15b are formed at both ends of the open side of the tube insertion side wall 15a so as to protrude outward and extend in the vertical direction.

  Further, the second member 16 has an anti-tube insertion side wall portion 16a facing the tube insertion side wall portion 15a, and the anti-tube insertion side wall portion 16a is curved so as to bulge outward from the header tank 5, and It is formed in a bowl shape that opens to the one member 15 side. The cross-sectional shape of the anti-tube insertion side wall portion 16a has an arc shape having a smaller curvature than the tube insertion side wall portion 15a. A pair of flanges 16b, 16b that protrudes outward and extend in the vertical direction are formed at both ends on the open side of the anti-tube insertion side wall 16a. The flange 16b of the second member 16 is formed flat so as to face the flange 15a of the first member 15 in a state where the second member 16 and the first member 15 are combined. That is, in this embodiment, the protrusions 17 that protrude outward from the outer peripheral wall of the header tank 5 to the upstream side and the downstream side in the air flow direction are configured by the flange 15b and the flange 16b.

  As shown in FIG. 3, tube insertion holes 15c corresponding to the outer shape of the tube 2 are formed in the first member 15 corresponding to the interval between the tubes 2, and the end of the tube 2 is the periphery of the tube insertion hole 15c. To be brazed. As shown in FIG. 4, the tube insertion hole 15c is formed in a slit shape extending from the central portion in the protruding direction of one flange 15b to the central portion in the protruding direction of the other flange 15b. The peripheral edge of the tube insertion hole 15c in the flange 15b of the first member 15 is formed so as to be recessed toward the side away from the flange 16b of the second member 16 facing the peripheral edge, thereby forming a recess 15d. Therefore, as shown in FIGS. 1 and 3, a space S is formed between the recess 15d and the flange 16b of the second member 16 facing the recess 15d. Further, the adjacent recesses 15d, 15d of the flange 15b of the first member 15 are formed flat so as to be joined to the flange 16b of the second member 16 to constitute a joint 15e. As shown in FIGS. 4 and 5, a circular through hole 15 f is formed at substantially the center of the joint 15 e.

  The distal end side of the flange 15b of the first member 15 is bent at a substantially right angle toward the flange 16b side at a portion corresponding to the distal end of the flange 16b of the second member 16. A piece-like caulking portion 15 g that is caulked and fixed to the flange 16 b of the second member 16 is formed at a portion corresponding to the joint portion 15 e on the distal end side of the flange 15 b of the first member 15. The first member 15 and the second member 16 are integrated by bending the caulking portion 15g along the surface of the second member 16 opposite to the joint surface of the flange 16b.

  The refrigerant path in the condenser will be described. First, an external refrigerant flows into the left header tank 5 from the refrigerant inflow pipe 11. The refrigerant flowing into the left header tank 5 flows into each tube 2 while flowing downward. The refrigerant flowing into each tube 2 is gradually condensed by exchanging heat with air while flowing through the tube 2 to the right side of the vehicle body, and gathers in the right header tank 6. Thereafter, the condensed refrigerant flows out from the refrigerant outflow pipe 12 to the outside.

  When manufacturing the condenser 1 configured as described above, first, the tubes 4 and the fins 3 are alternately arranged and fixed by a jig (not shown) to form the core 4, and the first member 15. And the 2nd member 16 is assembled | attached and the left side header tank 5 is comprised. When the left header tank 5 is configured, when the first member 15 and the second member 16 are combined, the joint 15e of the flange 15b of the first member 15 becomes the flange of the second member 16 as shown in FIG. 15b abuts. On the other hand, as shown in FIG. 1, a space S is formed between the recess 15 d of the flange 15 b of the first member 15 and the flange 16 b of the second member 16. In this state, the caulking portion 15g of the first member 15 is bent and the first member 15 and the second member 16 are caulked and fixed. The right header tank 6 is configured similarly.

  Thereafter, the cap members 10 and 10 are fitted into the openings at the upper and lower ends of the left and right header tanks 5 and 6. Both ends of the tube 2 of the core 4 are inserted into the tube insertion holes 15c of the header tanks 5 and 6, respectively. When the tube 2 is inserted into the tube insertion hole 15c, the end of the tube 2 protrudes from the flange 15b of the first member 15 toward the space S side and comes into contact with the flange 16b of the second member 16, and further insertion is performed. Movement in the direction is prevented. After assembling each member in this manner, although not shown in the figure, each member is fixed and integrated with a jig, and then carried into the furnace and heated, the brazing material melts and flows through the joint surface of each member. Brazing after cooling.

  In the brazing process, a force that separates the two members 15 and 16 may act on the first member 15 and the second member 16 due to vibration during loading into the furnace or deformation during heating. . At this time, since the first member 15 and the second member 16 are caulked and fixed, the positional displacement of these members 15 and 16 is prevented. In addition, since the caulking portion 15g is provided corresponding to the joint portion 15e of the flange 15b of the first member 15, the portions where both the flanges 15b and 16b are joined to each other are reliably brought into contact with each other, and the both flanges 15b and 16b. Can be brazed firmly.

  In the brazing process, the brazing material provided on the first member 15 melts and flows through the joint surface of the flange 15b. At this time, since the end of the tube 2 inserted into the tube insertion hole 15c protrudes from the flange 15b of the first member 15 toward the space S, the brazing material flowing through the flange 15b enters the opening of the end of the tube 2 Is avoided. Further, in order to determine the insertion position of the tube 2, the end portion of the tube 2 is brought into contact with the flange 16b of the second member 16, but the brazing material is not provided on the second member 16, This also prevents the brazing material from entering the opening of the end portion of the tube 2. By these things, it can prevent that the opening of the edge part of the tube 2 is block | closed with a brazing material, and can let the refrigerant | coolant of the header tank 5 flow into the tube 2 as aimed.

  In the condenser 1 obtained in this way, the inner diameter dimension in the air flow direction of the left and left header tanks 5 and 6 is set to be shorter than the width dimension of the tube 2. It can be made even smaller, and the refrigerant charging amount can be reduced. Thus, when the header tanks 5 and 6 are reduced in capacity, the width of the tube 2 can be secured longer than the inner diameter of the header tanks 5 and 6, and the heat transfer area of the tube 2 can be sufficiently obtained.

  And in the state which inserted the edge part of the tube 2 in the tube insertion hole 15c, except the part inserted in the part which continues to the flange 15b in the tube insertion hole 15c among the opening of the edge part of the tube 2, inside the header tank 5 Come to face. At this time, since the ratio of the inner diameter dimension of the header tank 5 to the width dimension of the tube 2 in the air flow direction is 0.7 or more, an area of 70% or more of the entire opening of the tube 2 faces the inside of the header tank 5. The refrigerant flows from this region. By setting the area of the opening of the tube 2 that faces the header tank 5 in this way, the amount of refrigerant flowing into the tube 2 is substantially reduced as compared with the case where the entire opening faces the header tank 5. Instead, the refrigerant flowing into the tube 2 flows over the entire width direction of the tube 2. Thereby, the expected refrigerant inflow amount can be secured and the heat exchange efficiency can be increased.

  Further, since the left header tank 5 is constituted by the combination of the first member 15 and the second member 16, the first member 15 and the second member 16 can be molded separately. Thereby, compared with the case where the tube insertion side wall part 15a and the anti-tube insertion side wall part 16a from which a shape mutually differs are shape | molded integrally in a cylinder shape, shaping | molding becomes easy.

  Moreover, since the tube insertion side wall part 15a of the 1st member 15 and the anti-tube insertion side wall part 16a of the 2nd member 16 are formed in the curved surface shape, when these 1st member 15 and the 2nd member 16 are combined, The entire peripheral wall portion of the header tank 5 forms a continuous curved surface. For this reason, pressure resistance can be obtained without increasing the thickness of the first member 15 and the second member 16, so that the header tank 5 can be reduced in weight. Furthermore, since the tube 2 is brazed to the periphery of the tube insertion hole 15c, the tube 2 and the tube insertion side wall 15a are integrated, and the strength of the tube insertion side wall 15a is increased. Therefore, the tube insertion side wall portion 15a can be formed flatter than the anti-tube insertion side wall portion 16a without increasing the thickness of the tube insertion side wall portion 15a. Thereby, the inner volume of the header tank 5 can be further reduced while reducing the weight of the header tank 5.

  Furthermore, in this condenser 1, after manufacture, it is test | inspected whether each brazing site | part is joined reliably. In this inspection, air pressurized to a predetermined pressure is introduced into the refrigerant inflow pipe 11 and the refrigerant outflow pipe 12. At this time, if the flange 15b of the first member 15 and the flange 16b of the second member 16 are not securely joined, air leaks from the through hole 15f formed in the flange 15b, and a brazing failure can be reliably detected. . Thereby, only the condenser 1 having the desired pressure resistance can be obtained.

  In this embodiment, the concave portion 15d is formed in the flange 15b of the first member 15, but the concave portion may be omitted as in Modification 1 shown in FIG. In this modification, the joining area between the flange 15b of the first member 15 and the flange 16b of the second member 16 is increased, and the joining strength is increased.

  In this embodiment, the recess 15d is formed in the flange 15b of the first member 15, while the flange 16b of the second member 16 is formed flat so as to form a space between the flanges 15b and 16b. However, the configuration may be reversed as in Modification 2 shown in FIG. That is, the recess 16d and the joint 16e are formed in the flange 16b of the second member 16, while the flange 15b of the first member 15 is formed flat. Further, a caulking portion 16 g is formed on the flange 16 b of the second member 16 and is caulked and fixed to the flange 15 b of the first member 15.

<< Embodiment 2 of the Invention >>
FIG. 8 relates to Embodiment 2 of the present invention. The condenser of this embodiment is configured in the same manner as the condenser of Embodiment 1 except for the shape of the tube 2 and the insertion position of the tube 2. In the following description, the same parts as those in the first embodiment are denoted by the same reference numerals, and only different parts will be described in detail. That is, in this embodiment, a pair of stepped portions 2a and 2a are formed on both ends in the longitudinal direction of the tube 2, and the stepped portions 2a and 2a are engaged with the periphery of the tube insertion hole 15c so that both ends of the tube 2 are The tube 2 is positioned with respect to the header tanks 5 and 6 so as to be away from the flange 16b of the second member 16.

  Specifically, stepped portions 2a and 2a formed to extend outward from the tube insertion hole 15c are provided at the insertion direction base end of the tube 2 on the insertion side end. The positions of the step portions 2a and 2a are such that when the tube 2 is moved in the direction of arrow B and inserted into the tube insertion hole 15c and engaged with the periphery of the tube insertion hole 15c, the end of the tube 2 is second. It is set not to contact the flange 16b of the member 16.

  Therefore, in the condenser 1 of this embodiment, as in the first embodiment, the capacity of the left and left header tanks 5 and 6 can be further reduced, the refrigerant charging amount can be reduced, and the heat transfer area of the tube 2 can be reduced. You can get enough.

  And in the state which inserted the edge part of the tube 2 in the tube insertion hole 15c, the location inserted in the part which continues to the flange 15b in the tube insertion hole 15c among the opening of the edge part of the tube 2 is the inside of the protrusion part 17. The other portions of the header tank 5 face the inside of the header tank 5. That is, the refrigerant in the header tank 5 flows into the tube 2 from the entire opening of the tube 2, so that the amount of refrigerant flowing into the tube 2 can be secured and the heat exchange efficiency can be improved.

  Further, since the step 2a of the tube 2 is engaged with the periphery of the tube insertion hole 15c to position the tube 2, the opening at the end of the tube 2 is a space without using a positioning jig or the like. The tube 2 can be positioned in a state where the tube 2 is reliably communicated with S. Thereby, the assembly | attachment operation | work of the tube 2 can be performed easily and reliably.

  The tube 2 is formed so as to have the same cross-sectional shape over both ends as in the first embodiment, and the end of the tube 2 is separated from the flange 16b of the second member 16 using a jig or the like. You may position as follows.

  Moreover, although each said embodiment has demonstrated the case where this invention is applied to the condenser of an air conditioner, this invention is applicable also to an evaporator, for example.

  As described above, the heat exchanger according to the present invention is useful as, for example, a condenser that constitutes one element of a refrigeration cycle of a vehicle air conditioner.

It is the sectional view on the AA line in FIG. It is the front view which looked at the condenser which concerns on embodiment of this invention from the air flow direction downstream. It is the elements on larger scale near the left side header tank. It is the side view which looked at the 1st member of the left header tank from the core side. FIG. 4 is a sectional view taken along line BB in FIG. 3. FIG. 6 is a view corresponding to FIG. 1 according to a first modification of the first embodiment. FIG. 6 is a view corresponding to FIG. 1 according to a second modification of the first embodiment. FIG. 3 is a view corresponding to FIG. 1 according to a second embodiment.

Explanation of symbols

1 Condenser (heat exchanger)
2 Tube 2a Stepped portion 5, 6 Header tank 15 First member 16 Second member 15a Tube insertion side wall 15b Flange 15c Tube insertion hole 15g Caulking portion 16a Anti-tube insertion side wall 16b Flange 17 Projection

Claims (9)

A plurality of flat tubes whose cross-sectional shapes are long in the air flow direction are juxtaposed in a direction crossing the air flow direction, and the end portions of these tubes are inserted into a cylindrical header tank extending in the tube juxtaposition direction to each tube. A heat exchanger that communicates with the inside of the header tank,
The header tank is formed such that the ratio of the inner diameter dimension of the header tank in the air flow direction to the outer dimension of the tube in the air flow direction is less than 1 and 0.7 or more,
The outer peripheral wall portion of the header tank is provided with a protruding portion that protrudes outward on the upstream side and the downstream side in the air flow direction, and a tube insertion hole that continues to the protruding portion. The heat exchanger characterized by the part being inserted. A plurality of flat tubes whose cross-sectional shapes are long in the air flow direction are juxtaposed in a direction crossing the air flow direction, and the end portions of these tubes are inserted into a cylindrical header tank extending in the tube juxtaposition direction to each tube. A heat exchanger that communicates with the inside of the header tank,
The header tank is formed such that the inner diameter dimension in the air flow direction is shorter than the outer dimension of the tube in the air flow direction,
The outer peripheral wall portion of the header tank is provided with a hollow protruding portion that protrudes outward on the upstream and downstream sides in the air flow direction and communicates with the inside of the header tank, and a tube insertion hole that is continuous with the protruding portion,
An end portion of the tube is inserted into the tube insertion hole so that the opening of the end portion communicates with the inside of the protruding portion. The heat exchanger according to claim 2,
At the proximal end of the insertion side end of the tube into the tube insertion hole, a stepped portion is provided extending outward from the tube insertion hole.
The tube inserted into the tube insertion hole is positioned so that the stepped portion engages with the periphery of the tube insertion hole and the opening at the end of the tube communicates with the inside of the protruding portion. Heat exchanger. In the heat exchanger as described in any one of Claims 1-3,
The end of the tube is brazed to the periphery of the tube insertion hole,
The tube insertion side wall portion of the header tank and the anti-tube insertion side wall portion facing the tube insertion side wall portion are formed in a curved surface shape that swells outward of the header tank, and the tube insertion side wall portion is the anti-tube insertion side wall portion. A heat exchanger characterized by a flatter shape. The heat exchanger according to claim 4, wherein
A header tank consists of a 1st member which has a tube insertion side wall part, and a 2nd member which has an anti-tube insertion side wall part, The heat exchanger characterized by the above-mentioned. The heat exchanger according to claim 5,
While the brazing material is provided in the contact surface with the 2nd member of a 1st member, the said 2nd member is not provided with the brazing material, The heat exchanger characterized by the above-mentioned. The heat exchanger according to claim 5 or 6,
The protruding portion that protrudes from the outer peripheral wall portion of the header tank is configured by a flange that extends opposite to the first member and the second member,
A tube insertion hole is formed continuously from the tube insertion side wall of the first member to the flange;
At least one of the peripheral portion of the tube insertion hole in the flange of the first member and the portion of the flange of the second member facing the peripheral edge of the tube insertion hole is formed in a concave shape so as to have a space between them. An end portion of the tube inserted into the tube insertion hole projects from the tube insertion hole and is positioned in the space. The heat exchanger according to claim 7,
At least one flange of the first member and the second member is provided with a caulking portion that is caulked and fixed to the other flange. The heat exchanger according to claim 8, wherein
The heat exchanger, wherein the caulking portion is provided corresponding to a portion where the flanges of the first member and the second member are joined to each other.

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